Shrimp-processing apparatus

ABSTRACT

An apparatus for processing shrimp and like marine life of the type utilizing a pair of horizontally extending, parallel rollers spaced apart a distance to accommodate a centerplate for defining a processing channel and also including an elongated impeller overlying an upper edge of the centerplate is characterized as having mechanical drive means including cams and eccentrics for operating the centerplate and the impeller from a single rotating line shaft. The cam means is arranged and configured to drive the centerplate and the impeller in undulatory patterns having both horizontal and vertical components of movement selected to operate on the marine life in conjunction with the rollers for peeling, deheading, deveining and otherwise cleaning the marine life and moving the same from an inlet end of the machine to a discharge end thereof. Further, the machine characteristics including cycle speeds, size and surface finish of the rollers and configuration of the centerplate have been optimized for most varieties of shrimp.

United States Patent Welcker et al.

[54] SHRIMP-PROCESSING APPARATUS [72] Inventors: Clyde J. Welcker; Roland Welcker, both of New Orleans, La.

[73] Assignee: The Welcker Corporation, New Orleans,

[22] Filed: Feb. 2, 1970 [21] Appl.N0.: 7,526

[ 1 Feb. 8, 1972 Primary ExaminerLucie H. Laudenslager AttorneyHill, Sherman, Meroni, Gross & Simpson [5 7] ABSTRACT An apparatus for processing shrimp and like marine life of the type utilizing a pair of horizontally extending, parallel rollers spaced apart a distance to accommodate a centerplate for defining a processing channel and also including an elongated impeller overlying an upper edge of the centerplate is characterized as having mechanical drive means including cams and eccentrics for operating the centerplate and the impeller from a single rotating line shaft. The cam means is arranged and configured to drive the centerplate and the impeller in undulatory patterns having both horizontal and vertical components of movement selected to operate on the marine life in conjunction with the rollers for peeling, deheading, deveining and otherwise cleaning the marine life and moving the same from an inlet end of the machine to a discharge end thereof. Further, the machine characteristics including cycle speeds, size and surface finish of the rollers and configuration of the centerplate have been optimized for most varieties of shrimp.

13 Claims, 9 Drawing Figures I I v I v I n I u I l v I i PATENTEU FEB em:

SHEET 2 0F 2 law Km mm Q w w% R m P LH Mum wm QQN Y NNWP H SHRIMP-PROCESSING APPARATUS BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates generally to an apparatus and method for processing shrimp, sardines and like marine life wherein the outer covering of the marine life is removed and inedible matter is massaged from the marine life, and more particularly refers to improved drive means for that type of apparatus.

2. Description of the Prior Art One type of apparatus for processing shrimp and like marine life generally includes a pair of horizontal parallel rollers spaced apart to receive an upper edge portion of a vertically extending plate. Opposite parallel side surfaces of the vertical plate cooperate with the rollers to define processing channels along which shrimp move during the cleaning operation.

The vertical plate is mounted for movement in a vertical plane and driven in an undulating cycle selected to cooperate with the rotating rollers for cleaning the shrimp and drawing the trash downwardly while simultaneously moving the shrimp horizontally along the rollers from an inlet end of the machine to a discharge end thereof. An elongated impeller member may be disposed above the centerplate for movement in the same vertical plane as the vertical plate. The impeller member cooperates with the other machine elements in cleaning the shrimp and particularly assists in propelling the shrimp along the rollers.

Heretofore, drive means for moving both the vertical plate and the impeller member through their respective undulatory cycles have included at least a pair of pneumatic or hydraulic cylinders appropriately actuated in a manner to move the plate and the impeller through the cycles. Due to inherent characteristics in that type of drive means, the prior art machines have limited cycle speeds, thereby decreasing efficiency of the machines. Further, since velocity and acceleration are difficult to control adequately with hydraulic and pneumatic cylinders, prior art machines have not operated smoothly.

Efficient cleaning of shrimp and like marine life depends upon several machine parameters including size and surface characteristics of the rollers, configuration of the upper edge of the vertical plate, angular velocity of the rotating rollers and cycle speed of the vertical plate and the impeller. Heretofore, appropriate values for those parameters have been alluded to but have not been attainable in a manner to provide an optimally configured machine.

SUMMARY OF THE-INVENTION In accordance with the principles of the present invention, a shrimp processing machine of the type utilizing a pair of horizontally extending, parallel rollers spaced apart a distance to accommodate a centerplate for defining processing channels and also including an elongated impeller overlying an upper edge of the centerplate is characterized as further comprising mechanical drive means for moving the centerplate and the impeller through undulating cycles having both horizontal and vertical components of movement.

The mechanical drive means includes a rotating line shaft supported in fixed bearing blocks secured to a frame of the machine and having at least one face grooved cam corotatably mounted thereon and at least one eccentrically mounted cylindrical surface formed thereon. The face grooved cam is connected to the centerplate and the overlying impeller and provides the vertical component of movement. In particular, the face grooved cam includes a 90 segment of increasing radius followed by a 90 segment of decreasing radius and a 180 segment of constant radius. The eccentrically mounted cylindrical surface or eccentric is received in a slotted plate, which in turn is connected to the centerplate and overhead impeller, in a manner to provide the horizontal component of movement. The eccentric cooperates with the slotted plate to advance and to retract the members for equal time segments, each corresponding to l rotation of the line shaft.

The mechanical drive means of the present invention is particularly arranged to provide smooth acceleration, deceleration velocity control and dynamic balancing, thereby eliminating unnecessary vibration inherent in drive means heretofore utilized for shrimp-processing machines.

It is also contemplated by the present invention to provide the rollers with an optimized length and surface finish characteristics. In that regard, we have discovered that with large, hard-shelled gulf shrimp, the majority of cleaning is accomplished within the first 20 inches of roller length, whereas very delicate Alaskan shrimp are generally cleaned in about 6 inches and are completely cleaned by the time they have traveled 20 inches along the rollers. Thus, the rollers of the present invention have a length greater than 20 inches, but not exceeding approximately 54 inches in length.

Additionally, the texture of the rollers along their length may be varied so that the majority of the cleaning is accomplished within the first 20 inches and damage to the cleaned meats as they travel along the remainder of the roller is minimized or eliminated.

It has also been discovered that different varieties of shrimp require different amounts of lubrication, and thus, the present invention includes means for introducing controlled quantities of water or other suitable lubricant into the input hopper and along the rollers.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. I is a partial top perspective view of an apparatus of the present invention with certain parts broken away and with the cover removed to illustrate mechanical drive means constructed in accordance with the present invention;

FIG. 2 is an elevational view of a face grooved cam forming a portion of the drive means of the present invention; FIG. 3 is an elevational view of an eccentric incorporated in the drive means of the present invention;

FIG. 4 is a side elevational view of the machine illustrated in FIG. 1 with parts broken away for clarity;

FIG. 5 is an end elevational view of rollers, a centerplate and an overlying impeller of the processing machine of the present invention;

FIG. 6 is a partial end view of a centerplate of the present invention and illustrates an alternative configuration for the centerplate top edge;

FIG. 7 is a view similar to FIG. 6 and illustrates another alternative configuration for the top edge of the centerplate; and

FIGS. 8 and 9 are graphs illustrating the undulating cycle, respectively, of the overlying impeller and the centerplate.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to the drawings, a shrimp, sardine and like marine life processing machine 10 has a pair of horizontally disposed rollers 11 and 12 spaced apart a predetermined distance to form a nip. Each of the processing rollers 11 or 12 has a coaxially disposed support shaft 13 extending from opposite end portions of the rollers and received in suitable bearing means for rotation about horizontally extending axes. Drive means as diagrammatically illustrated at M, in FIG. 1, rotate the rollers in opposite angular directions in a manner to massage marine life moving between the rollers and to peel the outer shell therefrom.

Cooperating with the rotating rollers 11 and I2 is a vertically disposed centerplate 14 having an upper edge portion I6 received within the nip defined between the pair of rollers. To assist the centerplate 14 in propelling the shrimp alo g the rollers, an impeller member 17 may be disposed above the centerplate upper edge 16. The impeller 17 cooperates with the rollers 11 and 12 and the centerplate 14 to advance the marine life from an inlet end 18 to an outlet end 19 of the nip or processing channels of the machine 10.

In accordance with the principles of the'present invention, mechanical drive means are provided for moving the center plate 14 and the impeller 17 smoothly through respective undulating cycles having both horizontal and vertical components of movement. A fixed platform 21 secured to the machine frame on angle members 22 mounts the mechanical drive means and supports the impeller 17 and the centerplate 14.

Means for mounting the centerplate l4 and the impelier 17 for movement in both horizontal and vertical directions include a first portion support on the platform 21 for vertical movement relative thereto and a second portion mounted on the first portion for horizontal movement therealong.

The first portion comprises a rectangular support platform 23 mounted for sliding movement on four upright posts 24. Each of the posts 24 has a lower end portion anchored in a base member 25 and an upper end portion slidably received in a slide bearing 26 mounted at one of the four comer portions of the support platform 23. The second portion of the mounting means comprise a pair of cross-machine channels 27, 27 supported on a pair of bars 28, 28 for horizontal sliding movement in directions parallel to the axes of the rollers 11 and 12. Each of the bars 28 is fixedly secured in a pair of mounting blocks 29, 29 disposed between the pair of channels 27, 27 and has opposite end portions 31 and 32, respectively, received within slide bearings 33 and 34 mounted within opposite ones of the channels. The support bars 28 are sufficiently spaced above an upper surface 36 of the platform 23 so that lower edge portions 37 of the channels 27 are maintained out of contact with the vertically movable support platform 23.

Thus, the support platform 23 is mounted for vertical movement in directions perpendicular to the axes of the rollers 11 and 12, whereas the channels 27 are mounted for free horizontal movement in directions parallel with the axes of the rollers 11 and 12.

A pair of vertically extending plates 38, 38 secured at opposite end portions of the channels 27, 27 suspend the centerplate 14 so that its top edge 16 is disposed within the nip between the pair of rollers 11 and 12. A pair of parallel bars 39, 39 extending parallel to the channels 27 27 have opposite end portions fixedly secured to the plates 38 and pass through the centerplate 14, thereby to fixedly secure the centerplate to the channels 27 so that vertical and horizontal movement of the centerplate is respectively coincidental to the vertical movement of the platform 23 and the horizontal movement of the channels.

It is also contemplated by the present invention to connect the impeller 17 to the vertically movable platform 23 and the channels 27 so that movement of the impeller in vertical directions is coincidental with movement of the centerplate l4 and horizontal movement of the impeller is in reverse directions to that of the centerplate and at approximately twice the amplitude. In order to provide that movement, the impeller 17 has opposite end portions 41 and 42 pivotally supported as at 43 and 44 on a pair of depending lever arms 46 and 47 respectively disposed near the input end 18 and the output end 19 of the machine 10. Each of the lever arms 46 or 47 is received between a pair of brackets 48 and 49 and has an aperture formed therethrough for receiving a pivot pin 51 which in turn has opposite end portions supported within the brackets 48 and 49. To move the impeller 17 coincidentally with the vertically movable platform 23, the brackets 48 and 49 are secured to a pair of oppositely extending plates 52, 52 fixedly attached to an underneath side of the platform 23.

Connecting arms 53 interconnect upper end portions 54 and 55, respectively of the lever arms 46 and 47 to opposite ones of the horizontally movable channels 27. Each of the connecting arms 53 has an inner end portion 56 attached to one of the channels 47 and a bifurcated outer end portion 57 straddling the lever arms 46 or 47 and pivotally pinned thereto as at 58. The apertures and the lever arms 46 and 47 for receiving the pivot pins 51 are disposed between the impeller connections 43 and 44 and the pivoted connection 58 at a point approximately one-third of the total distance from the upper pivotal connection 58. Thus, the impeller 17, the lever arms 46 and 47 and the connecting rods 53 form a parallelogram linkage arranged so that horizontal movement of the channels 27 in one direction drives theimpeller 17 in a direction opposite to the movement of the channels 27, and thus the centerplate l4, and through a distance approximately twice that of the centerplate,

In accordance with the principles of the present invention, mechanical drive means for vertically moving the platform 23 and horizontally moving the channels 27 relative to the platform include a line shaft 61, a pair of face grooved cams 62 receiving cam followers 65 secured to the platform 23 and a pair of eccentrics 63 received in elongated slots 64 formed in the end plates 38.

The line shaft 71 is driven via a variable speed drive by an appropriate motor M and is mounted within bearing blocks attached to the machine frame so that the shaft extends above the fixed platform 21 and beneath the vertically movable platform 23.

Each of the cam followers 65 includes a stub shaft 66 having a ball bearing.67 press fit on an outer end thereof and characterized by an outer ring sized to be fittingly received within a cam groove 68 formed in the cam 62. The stub shafts 66 extend parallel to the line shaft 61 and are attached via depending plate members 69 to opposite edge portions of the vertically movable platform 23.

As illustrated in FIG. 2, each of the face grooved cams 62 comprises a disc member having the cam groove 68v cut into a face thereof. An aperture 71 disposed eccentrically of a center of the disc receives the line shaft 61 so that the disc corotates with the line shaft. The cam groove 68 provides alternate vertical movement for I of rotation of the line shaft 61 and a dwell of l80,i.e., 180 of shaft rotation where there is no drastic vertical movement. In particular, the cam groove 68 has a first developed segment 72 extending through and having a gradually increasing radius measured from a center of the shaft 61, a second developed section 73 extending through the next 90 and having a decreasing radius, and a final, interconnecting segment 74 extending through and being formed at a relatively constant radius from the axis of the line shaft. Thus, as the cam 62 rotates in a clockwise direction the vertically movable platform 23, and thus the centerplate 14 and the impeller 17, will rise for 90 of rotation of the shaft 61, then fall during the next 90 of rotation and finally remain at a low point for 180 rotation of the line shaft in coincidentally reverse directions.

Referring now to FIG. 3, the eccentric means 63, which is received within the slots 64 in a manner to form a scotch yoke, comprise a disc 76 having an eccentrically disposed bore 77 characterized by a keyway 78. The line shaft 61 is received within the bore 77, and the disc is keyed to the shaft for corotation therewith. To provide a smooth motion and to eliminate vibration, the eccentrically mounted disc 76 is press fit within an inner ring 79 of an antifriction roller bearing having a plurality of bearing balls 81 and an outer ring 82. Each of the slots 64 formed in the end plates 38 has ahorizontal width sized relative to an outer diameter of the bearing outer ring 82 to closely receive the outer ring. The eccentrics 63 cooperate with the slots 64 to alternately move the channel members 27 in one direction for l80 of rotation of the line shaft and then to move the channel members in a reverse direction for the next 180 of rotation.

As graphically illustrated in FIGS. 8 and 9, the mechanical drive means of the present invention move the centerplate 14 and the impeller 17 through respective undulating cycles having a first segment corresponding to 90 of rotation of the line shaft 61, a second segment corresponding to the next 90 of rotation and a third segment during which the centerplate and the impeller are returned to a starting position during a final 180 of rotation of the shaft. As illustrated in FIG. 9, the center plate 14 rises between the counterrotating rollers 11 and 12 and advances therealong during a first segment 84 of its cycle. During a second segment 86 of the cycle, the centerplate continues to advance along the rollers 11 and 12 while falling toward its starting level. Finally, during a third segment 87 of the cycle, the centerplate is retracted along a relatively horizontal plane to its starting point.

Due to the parallelogram linkage defining the horizontal movement of the impeller 17, a first segment 88 of the impeller cycle, as illustrated in FIG. 8, corresponding to the first segment 84 of the centerplate cycle, includes a rising and retracting motion, wherein the impeller rises through the same distance as the centerplate but moves along the rollers 11 and 12 a distance equal to twice the movement of the centerplate. During a second segment 89 of the impeller cycle, the impeller 17 continues to move toward the input end 18 of the machine and falls toward the low point of the cycle. Finally, the impeller 18 advances along the rollers 11 and 12 at a relatively horizontal plane for 180 rotation of the line shaft, during a third segment 91 of its cycle to its starting point.

Thus, in that manner either the centerplate 14 or the impeller 17 is continuously propelling the shrimp or other marine life along the counterrotating rollers 11 and 12.

Shrimps are fed into the machine through an input hopper 93 disposed adjacent the input end 18 of the rollers 11 and 12. The hopper 93 receives a quantity of shrimp or other like marine life to be processed and has an aperture arranged to receive an upstanding tab 94 on the centerplate 14, which cooperates with the aperture to control the quantity of shrimp supplied. Sloping guide members 96 and 97, arranged to form a trough extending from the input hopper to the discharge end 19 of the rollers, direct the marine life into the nip formed by the processing rollers 11 and 12. Hopper 93 has a pulsating gate member 108 pivoted about a fixed point 110 on the marking frame and attached by pivoted linkage members 109 to lever arm 46 so as to be movable therewith.

In order to provide sufficient lubrication for the shrimp or other marine life, a spray head 98 is disposed within the input hopper 93 and directed in a direction to continuously spray water onto the shrimp in the hopper. Additionally, a plurality of spray heads as at 99 are disposed along the length of the rollers 11 and 12 to provide continuous lubrication for the shrimp being processed. Since different varieties of shrimp require different quantities of water or other lubricant, a control valve 101 is interposed between the spray heads 99 and a pressurized water source, thereby enabling control of the water supplied along the length of the rollers 11 and 12. The quantity of water controls the friction between the shrimp and the rollers 11 and 12, and generally, the more delicate Alaskan shrimp require more lubricant or water than the larger gulf shrimp to prevent damage to the more delicate shrimp.

It is also contemplated by the present invention to configure and structure the rollers 11 and 12 so that the rollers will clean both the delicate Alaskan shrimp and the larger gulf shrimp. It has been found that the large hard-shelled gulf shrimp are substantially cleaned within the first 20 inches of the rollers 11 and 12, whereas the smaller variety of shrimp, such as the Alaskan shrimp, are substantially cleaned in about 6 inches and are completely cleaned by the time they have been processed along 20 inches of the rollers. Further, most all varieties of shrimp are completely cleaned within 54 inches of travel along the rollers.

Thus, in accordance with the principles of the present invention, the rollers 11 and 12 have an axial length greater than 20 inches, but not exceeding approximately 54 inches.

In addition to the length of the rollers 11 and 12, their surface finish and resiliency determines the abrasiveness of the cleaning process as the shrimp move therealong. Thus, for the major cleaning operation occurring within the first 20 inches of the rollers 11 and 12,'the outer surface of the rollers should be composed of a soft, resilient surface having a relatively high coefficient friction and being provided with a relatively fine, helically spiral groove as at 102. To avoid mutilation of the cleaned meats while continuing to process the small percentage of shrimp not cleaned within the first 20 inches of the roller length, a transitional or medial section 103 is formed on the rollers 11 and 12. The medial section 103 may be a close textured or smooth yieldable rollers providing a lesser cleaning action than the first 20 inches of the rollers 11 and 12. Additionally, an output section 104 of the rollers 11 and 12, which extends for approximately 20 inches, should have a smooth hard surface, thereby providing a mild and unabrasive cleaning action to avoid damage to cleaned meats.

If desired, several pairs of short rollers with cooperating centerplates and impellers may be serially arranged or stacked so that more delicate shrimp may be processed through only one set of rollers while harder shelled shrimp may be processed through several sets of rollers as required for complete cleaning.

Another factor to be taken into consideration is the necessity of removing grit from the shrimp during the cleaning process and the necessity of slitting or opening the back of the shrimp. In this regard, it should be noted that with the hardshelled gulf variety of shrimp, back slitting and grit removal are necessary, whereas with the smaller Alaskan variety of shrimp there is little need for grit removal or back slitting. Since most of the back slitting and grit removal process is performed by the top edge 16 of the centerplate 14, the configuration of that edge may be varied in accordance with the type of cleaning necessary for the variety of shrimp being processed.

As illustrated in FIG. 5, the top edge 16 of the centerplate 14 tapers from the input end 18 of the machine 10 and toward the output end 19 thereof and is characterized by canted side edge portions 106 and 107 tapering upwardly to form a sharp edge capable of performing the back slitting and grit removal process. The sharp edge 16, as illustrated in FIG. 5, tends to mutilate the Alaskan variety of shrimp, and thus, either of the blunt edge portions 16a or 16b, as illustrated respectively in FIGS. 6 and 7, may be utilized with the Alaskan variety of shrimp. The edge portion 16a is particularly characterized as comprising a flattened section 108 having chamfered side edges 109 and 111. Further, as illustrated in FIG. 7, the blunt top edge portion 16b of the centerplate 14b has a smooth, convex arcuate cross section.

From the foregoing description, it will be noted that the shrimp processing machine 10 of the present invention includes a unique cam and eccentric drive means moving the centerplate 14 and the overlying impeller 17 through respective undulating cycles designed to massage and propel the shrimp along the counterrotating rollers 11 and 12. The processing rollers 11 and 12, which have a length in the range of 20 to 54 inches include a grooved, localized yieldable surface along the first 20 inches of their length followed by surfaces providing progressively milder cleaning action to prevent mutilation of cleaned meats. Further to enhance the cleaning operation and to promote movement along the rollers 11 and 12, spray heads are provided in the input hopper and along the length of the rollers to provide continuous lubrication during the processing operation. To further adapt the processing machine 10 to processing of different varieties of shrimp ranging from the very delicate Alaskan shrimp to the hard-shelled gulf shrimp, the configuration of the upper edge portion of the centerplate may be varied with a sharply tapered edge utilized for the hard-shelled shrimp and blunt edges utilized for the more delicate shrimp.

In a specific example of the present invention, the processing machine 10 included rollers having a diameter of 2.875 inches and being surfaced with resilient polyvinyl chloride. The eccentric 63 and the cam 62 were configured to provide a horizontal movement of 0.875 inches and a vertical movement of l .875 inches for the centerplate and a horizontal movement of L750 inches and a vertical movement of 1.875 inches for the overlying impeller 17. Further, the drive means for the rollers 11 and 12 were selected to rotate the rollers at rpm, whereas the line shaft was rotated to move the centerplate and the impeller through 58 c.p.m.

Although those versed in the art might suggest various minor modifications, it should be understood that we wish to embody within the scope of the patent warranted hereon all such modifications as reasonably and properly come within the scope of our contribution to the art.

We claim as our invention: 1. in a machine for processing shrimp, sardines and like marine life, the combination comprising:

a pair of horizontally extending, parallel, relatively rotatable processing rollers having input ends and discharge ends, said rollers having peripheral surfaces spaced apart to define a nip therebetween,

each said roller having an axial length exceeding 20 inches,

each of said rollers having locally resilient frictional surfaces formed with spiral grooves therein and extending for at least 20 inches from the input end of said roller;

means for counterrotating said rollers relative to one another;

a vertically disposed plate member having an upper edge portion mounted for vertical and horizontal movement between said pair of rollers;

impeller means overlying said plate upper edge and being mounted for vertical and horizontal movement relative to said plate member; and

mechanical drive means for driving both said plate member and said impeller through respective undulating cycles.

2. A machine as defined in claim 1 wherein said plate top edge portion has upwardly tapered side edge portions forming a pointed edge for contacting the marine life disposed within the nip.

3. A machine as defined in claim 1 wherein said plate top edge portion has a horizontal flat portion and chamfered opposed side edges.

4. A machine as defined in claim 1 wherein said plate top edge portion has a convex arcuate configuration in transverse cross section.

5. A machine as defined in claim 1 and further characterized by:

means forming an input hopper mounted adjacent the input ends of said rollers; said hopper having a movable wall mechanically associated with said drive means for regulated movement;and

means continuously spraying a lubricating fluid onto marine life contained in said input hopper to enhance relative sliding movement of the marine life against one another.

6. A machine as defined in claim 1 and further characterized by:

means disposed along said rollers and continuously spraying a lubricating fluid onto the marine life moving along the nip; and

control means for varying a quantity of the fluid supplied by said spray means.

7. In a machine for processing shrimp, sardines and like marine life, the combination comprising:

a pair of horizontally extending, parallel, relatively rotatable processing rollers spaced apart a distance to form a nip therebetween and having input ends and output ends;

means forming a vertically disposed plate extending substantially parallel with axes of said rollers;

means forming an impeller member overlying and vertically spaced from a top edge portion of said plate;

means forming a fixed frame;

means mounting said rollers on said frame;

means mounting said vertically disposed plate and said impeller member on said frame for vertical movement relative to said rollers and for horizontal movement in directions parallel to the axes of said rollers;

drive means for propelling said centerplate and said impeller through respective undulating cycles having components of movement in both vertical and horizontal directions, said drive means including a rotating line shaft supported on said frame,

cam means driven by said line shaft and coincidentally moving said vertically disposed plate and said impeller member in vertical directions, and eccentric means having a cylindrical surface eccentrically 5 mounted on said line shaft for rotation therewith and means cooperating with said cylindrical surface for moving said plate member and said impeller in horizon-' tal directions along said rollers. 8. In a machine as defined in claim 7 and further charac- 10 terized by:

said mounting means including a first portion mounted on said frame for vertical movement relative thereto,

a second portion mounted on said first portion for vertical movement therewith and for horizontal movement relative thereto,

said plate member being connected to said second portion for horizontal and venical movement therewith,

said impeller member being connected to said first portion for vertical movement therewith, and

connecting means interconnecting said impeller and said second mounting portion so that said impeller horizontally moves in opposite directions to movement of said plate and at twice the amplitude of the plate horizontal movement.

9, A machine as defined in claim 8 and further characterized by:

said connecting means including a pair of horizontally spaced, depending arm portions having upper and lower end portions and being mounted for pivotal movement about horizontally extending pivot axes relative to said second portion,

said impeller mounted at lower end portions of said arms for pivotal movement relative thereto, and

rigid means connected at upper end portions of said lever arms for pivotal movement relative thereto and connected to said second portion for horizontal movement therewith.

4 10. A machine as defined in claim 8 and further characterized by:

said means cooperating with said eccentrically formed cylindrical surface including means connected to said second portion and having a pair of parallel, spaced horizontal wall portions engaging diametrically opposite peripheral edge portions of said cylindrical surface so that said second portion is alternately advanced toward the output ends of said rollers and retracted toward the input ends of said rollers.

11. A machine as defined in claim 10 and further characterized by:

said cam means being configured to alternately move said first portion upwardly and downwardly of said rollers while said eccentric advances said second portion and to hold said first portion in a constant lower horizontal plane while said eccentric means retracts said second portion. 12. A machine as defined in claim 11 and further characterized by:

said cam means including means forming a cam groove for receiving a cam follower connected to said first portion. 13. A machine as defined in claim 8 and further characterized by:

said eccentric means cooperating with said spaced, vertical wall portions to advance said second portion toward the output ends of said rollers for 180 of rotation of said line shaft and to retract said second portion for a next 180 of rotation of said line shaft; and said cam means having a first 90 segment and a second 90 segment vertically moving said second portion while said eccentric advances said first portion, said first cam segment formed at increasing radial distances from an axis of said line shaft, and said second segment continuing from said first segment and being formed at decreasing radial distances from the axis of said line shaft,

a third cam segment formed at a constant radial distance from the axis of said line shaft and controlling vertical movement of said first portion during retraction of said second portion by said eccentric means. 

1. In a machine for processing shrimp, sardines and like marine life, the combination comprising: a pair of horizontally extending, parallel, relatively rotatable processing rollers having input ends and discharge ends, said rollers having peripheral surfaces spaced apart to define a nip therebetween, each said roller having an axial length exceeding 20 inches, each of said rollers having locally resilient frictional surfaces formed with spiral grooves therein and extending for at least 20 inches from the input end of said roller; means for counterrotating said rollers relative to one another; a vertically disposed plate member having an upper edge portion mounted for vertical and horizontal movement between said pair of rollers; impeller means overlying said plate upper edge and being mounted for vertical And horizontal movement relative to said plate member; and mechanical drive means for driving both said plate member and said impeller through respective undulating cycles.
 2. A machine as defined in claim 1 wherein said plate top edge portion has upwardly tapered side edge portions forming a pointed edge for contacting the marine life disposed within the nip.
 3. A machine as defined in claim 1 wherein said plate top edge portion has a horizontal flat portion and chamfered opposed side edges.
 4. A machine as defined in claim 1 wherein said plate top edge portion has a convex arcuate configuration in transverse cross section.
 5. A machine as defined in claim 1 and further characterized by: means forming an input hopper mounted adjacent the input ends of said rollers; said hopper having a movable wall mechanically associated with said drive means for regulated movement; and means continuously spraying a lubricating fluid onto marine life contained in said input hopper to enhance relative sliding movement of the marine life against one another.
 6. A machine as defined in claim 1 and further characterized by: means disposed along said rollers and continuously spraying a lubricating fluid onto the marine life moving along the nip; and control means for varying a quantity of the fluid supplied by said spray means.
 7. In a machine for processing shrimp, sardines and like marine life, the combination comprising: a pair of horizontally extending, parallel, relatively rotatable processing rollers spaced apart a distance to form a nip therebetween and having input ends and output ends; means forming a vertically disposed plate extending substantially parallel with axes of said rollers; means forming an impeller member overlying and vertically spaced from a top edge portion of said plate; means forming a fixed frame; means mounting said rollers on said frame; means mounting said vertically disposed plate and said impeller member on said frame for vertical movement relative to said rollers and for horizontal movement in directions parallel to the axes of said rollers; drive means for propelling said centerplate and said impeller through respective undulating cycles having components of movement in both vertical and horizontal directions, said drive means including a rotating line shaft supported on said frame, cam means driven by said line shaft and coincidentally moving said vertically disposed plate and said impeller member in vertical directions, and eccentric means having a cylindrical surface eccentrically mounted on said line shaft for rotation therewith and means cooperating with said cylindrical surface for moving said plate member and said impeller in horizontal directions along said rollers.
 8. In a machine as defined in claim 7 and further characterized by: said mounting means including a first portion mounted on said frame for vertical movement relative thereto, a second portion mounted on said first portion for vertical movement therewith and for horizontal movement relative thereto, said plate member being connected to said second portion for horizontal and vertical movement therewith, said impeller member being connected to said first portion for vertical movement therewith, and connecting means interconnecting said impeller and said second mounting portion so that said impeller horizontally moves in opposite directions to movement of said plate and at twice the amplitude of the plate horizontal movement.
 9. A machine as defined in claim 8 and further characterized by: said connecting means including a pair of horizontally spaced, depending arm portions having upper and lower end portions and being mounted for pivotal movement about horizontally extending pivot axes relative to said second portion, said impeller mounted at lower end portions of said arms for pivotal movement relative thereto, and rigid means connected at upper end portions of said lever arms for pivotal movement relative thereto and connected to said second portion for horizontal movement therewith.
 10. A machine as defined in claim 8 and further characterized by: said means cooperating with said eccentrically formed cylindrical surface including means connected to said second portion and having a pair of parallel, spaced horizontal wall portions engaging diametrically opposite peripheral edge portions of said cylindrical surface so that said second portion is alternately advanced toward the output ends of said rollers and retracted toward the input ends of said rollers.
 11. A machine as defined in claim 10 and further characterized by: said cam means being configured to alternately move said first portion upwardly and downwardly of said rollers while said eccentric advances said second portion and to hold said first portion in a constant lower horizontal plane while said eccentric means retracts said second portion.
 12. A machine as defined in claim 11 and further characterized by: said cam means including means forming a cam groove for receiving a cam follower connected to said first portion.
 13. A machine as defined in claim 8 and further characterized by: said eccentric means cooperating with said spaced, vertical wall portions to advance said second portion toward the output ends of said rollers for 180* of rotation of said line shaft and to retract said second portion for a next 180* of rotation of said line shaft; and said cam means having a first 90* segment and a second 90* segment vertically moving said second portion while said eccentric advances said first portion, said first cam segment formed at increasing radial distances from an axis of said line shaft, and said second segment continuing from said first segment and being formed at decreasing radial distances from the axis of said line shaft, a third cam segment formed at a constant radial distance from the axis of said line shaft and controlling vertical movement of said first portion during retraction of said second portion by said eccentric means. 